Pump



May 11,1949. C.W.MQ1'I' 2,410,220

. m Filed Sept. 11, 1943 v 7 Sheetsk-Shet 1 May PUMP

Filed Sept 11 943 7 sheet fl 2 c. w. MOTT 7 May 17, 1949.

PUMP 7 Sheets-Sheet 4 Filed Sept. 1-1, ,1943

May 17, 1949. c. w. MOTT PUMP Filed Sept. 11, 1943 7 Sheets-Sheet 5 v l5g 0. w'. MOTT May 17, 1949.

PUMP

7 Sheets-Shet 6 Filed Sept. 11, 1943 f ay 37, 1949. c. w. MOTT 2,470,220

PUMP

Filed Sept. 1;, 1943 '7 Sheets-Sheet 7 enema May 11, 1949v UNITED STATESCarl W. Mott, La Grange, asslgnor to Inter- .7 national HarvesterCompany, a corporation of New Jersey Application September 11, 1943,Serial No. 501,985 u This invention has to do with pumps of the rotarytype and with a pump employing a rotor in which pistons are'reciprocatedwith a pumping action in timed relation with such rotor. The rotorcylinders or pump chambers and the pistons therein are revolved aboutparallel eccentrically disposed axes to obtain'reciprocation of thepistons relatively to and within the cylinders without incurringreversible movement of either the cylinders or pistons.

A general object of the invention is the provision of a compact pumpoperable at high-speeds to deliver fluid at a substantial flow rate, andcapable of high pressure delivery at both high and low speeds,

Another object is the provision of a novel port and passage arrangementby means of which fluid is drawn into and expelled from the pumping unitwith but a small flow resistance.

Another object is the provision of an improved rotary pump having arotor with radially directed cylinders in which pistons are operablewith a sinusoidal movement inwardlyby force imparted thereto by a camand outwardly by centrifugal force or by centrifugal force augmented bythe pressure of fluid pumped by the device. This construction obtainsnoiseless shockless operation without the use of springs or articulatelyconnected parts, minimizing the weight of the revolved parts and in allconducive to driving of the unit at high speed.

Another object is the provision of a novel pis-' ton-actuating memberhaving an arcuate surface eccentrically embracing the rotor to force thepistons radially inwardly during the discharge phase in the rotor cycle,and bearing means for rotatively supporting the actuating member so itcan rotate as the pistons revolve and thereby diminish the relativemovement between said member and the pistons. This diminishes wear uponslidingly engaging surfaces on the pistons and on the piston-actuatingmember, and the wear upon these surfaces is further reduced by curvingthe piston surfaces so that the line" thereon of contact with thesurface of the actuating member shifts to disperse the wear and heat.

Another object is the provision of a communication between the intakepassage and the casing chamber enclosing the sliding surfaces of thepistons and their actuating member, so that fluid may occupy thischamber to lubricate the sur-' faces and various bearings of rotatableparts, and so part of this fluid may be that leaking past the pistons.

Another object is the provision of a novel rotor wherein the bottoms ofthe radial cylinders are 20 Claims. (Cl. 103-161) 2 countersunk toreceive tail portions of the pistons and to receive fluid for urging thepistons outwardly. The centrifugal force is thus as sisted in itsmovement of the pistons, and the pistons are also movable outwardly bysuch fluid pressure at slow speeds at which the centrifugal force wouldbe insufficient to move the pistons. It is possible, therefore, tooperate the pump as slowly as desired.

These piston tails also furnish piston stabilization, making it possibleto make the main bodies of the pistons shorter and to place the bottomsof their cylinders nearer to the center of the rotor, whereby thediameter and mass of the pump is tremendously diminished.

A further object is the provision of a ported member together with novelmeans for pressing it in sliding sealing relation with a ported end faceof the pump rotor to separate inlet and outlet passages whichcommunicate with the rotor ports during respective periods in eachrotation of 'the rotor. The invention also has as one of its objects theprovision of a new wall structure having said sealing memberincorporated thereinto and rotatively adjustable to reposition saidmemher and the inlet and outlet passages of the pump so that thedirection of flow through these passages will be unaltered when thedirection in rotation of the pumping unit is changed.

A further object is the provision of means for utilizing the outlet highpressure fluid for imposing force upon said sealing member to press itagainst the rotor end face and thus'compensate for wear between thefaces of said member and rotor.

An additional object of the invention is the provision of a cone-shapedend face for the pump rotor for receiving a ported sealing memberrelatively to which-the rotor rotates and into and from which the fluidis discharged and drawn through the rotor ports.

Still another object is to employ a cone-shaped sealing member as in thenext preceding object as .a bearing support for the rotor and cooperablewith means for axially adjusting the rotor to take up any loosenessdeveloped between the sliding conical surfaces because of wear. Thisadjusting feature also makes it possible to adjust to overcome widertolerances of error in manufacture.

These and other desirable objects inherent in and encompassed by theinvention will be more structed according to invention;

Fig. 2 is an end elevation of the pump shown in Fig. 1, looking towardthe-left end of said pump as viewed in Fig. 1;

Pig, 3 is a fragmentary sectional view taken on the line} .91 Fig. 2 toillustrate inlet and outlet passages in the casing end wall structure;

Fig. 4 is a transverse sectional view taken through the pump at thatsection containing the rotor, as indicated by the line 4 in Fig. 1; Fig.5 is a transverse sectional view taken at the line 6 in Fig. 1 toillustrate the position and shape of inlet and outlet ports in a sealingmember which is pressed in sliding sealing relation with an end of therotor;

.Fig. 6 is a fragmentary, longitudinal, sectional view similarly to Fig.1 through a modified form of the invention which, employs ball membersfor Fig, Tis a longitudinal sectional view taken centrally through athird form of the invention;

Fig. 8 is a transverse sectional view taken through the pump rotor, asindicated by the line I in F18. "I; I

Fig. 9 is a transverse sectional view taken in the opposite direction toFig. 8 and illustrating ports, fastening means, and the disposition ofan end wall sealing member for the pump rotor;

Fig. 10 is a view taken like Fig. 9 on the line III of Fig. '7 tofurther illustrate the aforesaid ports, fastening members, and sealingmember;

Fig. 11 is a longitudinal sectional view taken centrally through afourth embodiment of the invention;

Fig. 12 is a transverse sectional view taken through the rotor upon theline l2 of Fig. 11;

Fig. 13 is a transverse sectional view taken in the opposite directionto Fig. 12 for illustrating ports, fastening means, and an end wallsealing member which is pressed in sliding sealing relation with an end.of the rotor;

Fig. 14 is a sectional view taken on the line I4 of Fig. 11 to furtherillustrate the parts shown in Fig. 13;

Fig. 15 is a fragmentary sectional view taken on the line ii of Fig. 13,showing in detail plungers which'are urged by the pressure of fluid inthe pump outlet passage against the sealing member for pressing itfirmlyin sliding sealing relation with the pump rotor;

Fig. 16' isa sectional view taken axially and centrally through. anotherembodiment of the invention; and

Fig. 1'! is an end view of a conical port-sealing member employed inthis final embodiment of the invention: a

With continued reference to the drawings, and particularlyto Figs. 1 to5, the casing in for the pump can be seen :to be generally cylindrical.

The right end of thecasing as viewed in Fig. 1 is closed by anend platell having a cylindrical reentrance portion I22 containing a bearing i3for the receptionaandi support of :a drive shaft l4 formedintegrally-with a--:rotor IS. The opposite end ofxth'e :casingfll is.aclosed bya casing end plate; i6 which. is-iheld: in place .by machinebolts ll.- =-Inlet-. and exhaust-sports...respectively desig-..nated-.-l8and:;i9,'are-formedrin the casing end .plate :16;-

intermediate wall -of the casing,

generally designated .:.2-l,-,:forms one end of a chamber 22 containingthe rotor l5 and other movable parts of the" pump unit 23. This wall 2!comprises a portion 24 formed integrally with the casing and havinga'cylindrical surface 25 the principles of the 4 in which a sealingmember 26 is axially adjustable. Said sealing member has an innersealing face 21 for bearing in sliding sealing relation with a portedend face 28 of the rotor. The cylindrical periphery of a hole 29 in thesealing member 26 rotatively receives and is in sealing relation with aspindle 3! formed integrally with and projecting endwise from the rotorI5. Rotation of the sealing member 26 is prevented by a pin 32 insertedthrough a hole 33 in the casing and into a recess 34 in said sealingmember.

Pressure of the desired amount between the slidingly engaged surfaces 21and 28 on the sealing member 26 and the rotor 15 is maintained by 1.bearing member 35, a washer 36, and a castellated nut 31 havingcastellations 38, which is screwed onto a threaded section 39 of thespindle 3|. A cotter key 4| inserted through the spindle 3| iscooperable with the castellations 38 for maintaining the desiredadjustment.

Pistons 42 in respective radial cylinders 43 of the rotor are urgedcentrifugally outwardly, during rotation of the rotor, against thecircumscribing bearing surface 43 upon the inner side of a I from theircylinders.

cylindrical piston-actuating member 44. This member 44 is jourrialed bymeans of a ball hearing unit 45 upon the outer periphery of the cats ingreentrant portion 12 to dispose the surface 43, which is perfectlycircular in the form illustrated, eccentrically of the rotor axis.Therefore, as best illustrated in Fig. 4, as the rotor rotates, thecircular surfac 43 will permit the centrifugal force to move the pistonsradially outwardly during one-half of a revolution of the rotor and willserve to force the pistons radially inwardly against the urge of thecentrifugal force during the succeeding half revolution.

Ports communicate between bottom portions of the cylinders 43respectively and the end wall face 28 of the rotor, and the sealingmember 26 is so oriented circumferentially of the rotor axis withrespect to the offset in the eccentricity of the piston-actuator ring ormember 44 that an arcuate inlet port 41 in the face 21 of said sealingmember will be traversed by each port 46 while the associated piston ismoving radially outwardly, and that an arcuate outlet port 48 istraversed by each port 46 while its associated piston is being forcedinwardly by the arcuate member 44. In other words, as best conceived byreference to Figs. 4 and 5, during rotation of the rotor, the rotorports 46 which are spaced circumferentially about the rotor axis arerevolved about this axis when the rotor is rotated and, during oneportion of the circular path of revolution of these ports, theirassociated pistons will be caused to move radially outwardly for drawingfluid into their cylinders and, during a succeeding portion of the pathof revolution, the pistons are forced inwardly to expel the fluid Thatportion of the path traversed by the ports 46 during outward movement ofthe pistons is the inlet path portion, whereas that traversed by theports during inward movement of the pistons is the discharge pathportion. The inlet path portion for the ports 46 coincides with thearcuate inlet port d1, Fig. 5, while the outlet path portion iscoincident with the arculate outlet port 48 in the sealing member 26(Fig. 5).. Oriented assembly of the sealing member 26 with respect tothe direction of eccentricity of the piston-actuating member 44 isassured and expedited by the pin 32 and the sealing member recess 34which recelves said pin when the sealing member is properly oriented.

In Figs. 3 and 5, the'linlet'port 41 can be seento enlarge in itsdiameter as it approaches the outer or left side of the sealing member26 as viewed in Fig. 3, making thls'port correspond generally to theportion of a side wall of a cone.

vA chamber 49 between the end' plate l6 and the sealing wall 21provides'communication be- 6 tween the inlet ports 18 and 41, Fig. l.Communication between the outlet ports l9 and 48 is pro- I vided by anoutlet channel 5|, Fig. 3. Provision is made-for utilizing .thepressure.of the pump fluid for augmenting the centrifugal force in urging thepistons outwardly against the eccentric piston-actuating member 44.InFigs. l and 4, cylinders 43 can be seen to be counterbored at 52 andthese counterbores communicate orv intersect to form a chamber 53 in acentral position within the rotor. Cylindrical tails 54, formedintegrally with the pistons, slide radially within the bores 52 whileblocking the communication between the chamber 53 and the cylinders 43.

A lateral channel 55 (Fig. 1) communicates between the rotor chamber 53and the groove 56 circumscribing the route of the spindle 3|. A shortchannel 51' (Fig. 5) inthe face 21 in the sealing member 26' providescommunication between the outlet port 48 and the groove 56, whereby,during operation of the pump, fluid at high pressure in the outlet port48 'will be forced inwardly through the channel 51, groove 56, andchannel 55 to the chamber 53 for forcing the pistons 42 against theactuator ring 44. This expedient for applying pressure into the chamberthrough the inlet port I 8, inlet chamber-43, and the ports 41 and 48,Radial outward movement of the piston will continuepntll it reaches theposition of the uppermost piston in Fig. 4 and, during the most of thismovement, the associated port 46 will be in. registry'withithe inletport 41, so that, during all ofjthlstime, fluid, will be drawn into thecylinder throughfthe' inlet ports and passages, whereby that portion ofthe cylinder. beneath the piston will be. filled with fluid. As thefilled cylinder rotates counter-clockwise from theuppermost position inFig. 4, its piston 42 will be forced gradually inwardly by the operatingmember 44 and, during thisv time, the port 46 will register with theexhaust port 48 in the sealing member 26, so that, while the pistonmoves from the uppermost position to the lowermost position, the fluidwill be expelled through the arcuate port 48, the channel 5| (Fig. 3),and outwardly through the-discharge port 19. Because of the plurality ofpistons and cylinders, some of the ports 46 are constantly-communicativewith'the'inlet port 41 and likewise some of the ports 46 are constantlycommunicative with the port 48, so that there is a continuous flow offluid inwardly through the port 41 and outwardly through the port 48.

ing the firm sliding contact between these faces.

Such adjustment is made by removing the cotter pin 4! and rotating thecastellated nut 31 for advancing the parts 26, 35, and 36 toward therotor. When the desired firmness of' contact is obtained between thefaces'21 and 28, the rotation of the nut 31 will cease and'the cotterpin 3i will be reinserted for maintaining the adjustment.

The operation is as follows:

The sealing member 26 is so oriented with respect to the eccentricdisplacement of the pistonactuating member 44 that the pump will operateto draw in fluid through the inlet port It! (Figs. 1 and 2) and to expelfluid through the outlet port 19 (Figs. 3 and 2) when the rotor isrotated in the direction of the arrow in Fig. 4. While the piston 42 isin the lowermost position in Fig. 4, it will occupy its most inwardposition radially of the rotor. As the rotor rotates in thecounterclockwise direction as viewed in Fig. 4, the piston in thelowermost position will have a tendency to move radially outwardly undercentrifugal force and the pressurefluid upon the inner end of its tailportion. When the port 46 associated with this piston arrives inregistry with the lower end of the inlet port 41 (Fig. 5), the pistonwill have been moved outwardly far enough to have created a low pressurein the bottom of its cylin der, causing fluid to be drawn into thecylinder The speed at which the pump'may be operated 'is increased bymaking the surface 43 on the actuator member 44 circular so that asinusoidal movement is'imparted to the pistons 42. Operating speed isalso possible in the higher range because of the very slight relativemovement required between the outer ends of the pistons and theactuating member 44. This member 44 is freely rotatable upon the ballbearing unit 45, so that it is caused to rotate with "the rotor l5,because of the frictional engagement of the pistons with said member.Therefore, during half of a revolution from one horizontal position tothe other. the outer end of each piston will have slid or crept from aline of contact slightly to one side of the piston axis to a line ofcontact a short distance on the other side thereof, and during thesucceeding half revolution, each piston shifts its line of contactacross the piston axis back to the initial point. It should be notedthat, because of the curved outer end contour of these pistons, the lineof contact between the piston and the piston-actuating member 44 isconstantly changing, wherefore the pressure upon the piston is notconstantly localized. Consequently the heat of friction generatedbetween the pistons and the actuating member 44 is dispersed overasubstantial area at the end of the piston and, of course, over theentire circumferential area of the surface 43.

' Constant lubrication-of the curved outer end surfaces of the pistonsand of the actuator member surface 43 is also conducive to high speedoperation. The fluid, such as oil, which is pumped by the device willleak to a slight degree outwardly past the pistons into the chamber 22,and some of this fluid which is suitable for lubrication will alightupon the surface 43. Some of the lubricating fluid will also get intothe hearing unit 45 for lubricating the same. Excess fluid leakage pastthe pistons into the chamber 22 can escape into the inlet chamber 49through a passage 59 in the wall structure 2|. While the pump is at restthe fluid level of a'liquid in the chambers 49 and 22 will tend toequalize through the communication 49, causing the fluid, such as oil,to rise sufllciently far in the chamber 22 to ton can, therefore, bemade of greater diameter and shorter stroke and placed sufliciently nearthe axis of the rotor so that the pump has a relatively small diameter.In this manner the weight of both the rotor and the pistons becomes lessto adapt the pump for high speed operation.

That form of the invention shown in Fig. 6 has parts which for the mostpart are like those shown in'Fig. 1, and, to expedite this description,corresponding parts are indicated by the same respective referencecharacters with the addition of the letter a. This second form of whileobtaining adequate stabilization. The pisthe invention employs sphericalmembers 42 for the balls are provided with no tails, as 54, on

the pistons 42 and, of course, no bores, as 52,

respective threaded holes 68 in said ring. After the ring 63 has beenrotated into position for orienting the sealing member structure 26''with respect to the outlet portion of the path traversed by the ports 46in the rotor, the bolts 62 will be tightened for drawing the member 6|into abutment with the end of the casing wall,

whereby the threads on the outer periphery of v the ring 63 are pulledaxially against the threads against rotation and to thereby maintain theoriented position of the sealing member 26. 'A plate 69 of suitablebearing metal is employed as a facing for the inner end of the bearingstructure 26' and this plate is pressed into sliding sealing relationwith a facing bearing plate H forming the end face of the rotor IS. Aplurality of dowel pins 12 hold the bearing plate H for rotation withthe rotor, and similar pins (not shown) are employed for holding thefacing plate 69 in assembly with the structure 26". Holes 13 in. thefacing plate ll register with the ports 46*, and an arcuate outlet port48 in the bearing plate 69 communicates with a channel 14 which extendsthrough the stem 65 of the sealing member structure 26 The outletpassage continues from the channel 14 through a or chamber, as 53, areformed in the rotor l5".

These pistons in the form of balls 42 have the advantage of economicalproduction, and the further advantage of being adapted to roll upon theinner periphery of the actuating member 44, so that no sliding takesplace between the actuating member 44' and the balls 42. The operation'of this second embodiment, with the exception of the fluid pressurecomponent of force for urging these balls radially outwardly, isidentical to the operation described above for the first embodiment.

The third embodiment shown in Figs. '7 to 10 operates upon the sameprinciple as the first and second embodiments. Consequently, to expeditethe description, corresponding parts are desigton-actuating member 44 isjoumaled directly' on a cylindrical section 60 of the casing which isarranged eccentrically to the rotor axis, as shown in Fig. 8. The inletport l8 is formed in an end plate I6 which is secured by bolts H to aplate-like holder member 6| for a sealing member structure 26 Additionalbolts 62 are employed for securing the holder member 6| to an annular,externally threaded retaining ring 63. The threads on this ring 83 meshwith threads 66 upon an internal portion of the casing. In assemblingthat part of the casing wall structure to the left of the rotor l5, asviewed in Fig. '7, the retaining ring or member 63 will first be screwedinto the threads 64 to a position approximating that shown in thedrawing. Following this, the ported sealing structure 26 will beassembled with the holder member 6! therefor by the insertion of aported stud 65 on the structure 26 into an opening 66 in-the member 6|.The bolts 62 will be inserted through holes 51 in the member 6!preparatory to this member being carried into axial alinement with thering 63 and the turning of the bolts 62 into channel 15 in the end plateI6 to the outlet port IS The inlet passage leads from the inlet port l8through a large hole I6 in the holder member 6| and a space 11 in thering 63 below a lower chordal edge I8 of the sealing member structure 26(see Figs. 9 and 10).

Initial pressing of the bearing plate 69 against the bearing plate H onthe end face of the rotor is accomplished by a headless set-screw 8 I,of which the groove 82 for receiving the bit of a screwdriver isaccessible through a hole 83 in the end plate l6' when a screw-plug 84is removed. This set-screw 8| is adapted to bear against the outer endof the stem, and to thereby establish a firm pressing relation betweenthe bearings plates 69 and II. After the pump is in operation thepressure of fluid discharged from the rotor into the channel 15 isutilized to augment the force of the screw 8! for pressing the sealingstructure upon the outer end of the stem 65 for pressing 26 against therotor. Pressure of such fluid acts upon the outerend of the stem 65 forpressing said sealing'structure to the right. A sealing member 85 isdisposed in a recess 86 into which the outer end of the stem 65 projectsto prevent leakage of fluid from the high pressure channel '35 betweenthe stem and the hole 66 therefor in the holder M. A small leakage whichwill occur simply advances downwardly between an inner face 81 of theholder 6| and an outer face 88 of the sealing member structure into thepump inlet passage for reintroduction into the pump unit.

It should be noted that the exhaust passage communicates with thebearing surface 60 for the piston-actuation member 44 through a smallspace 89, and further that the fluid in the passage communicates withthat part of the casing enclosing the bearing units l3 through the spaceSt between the rotor and the piston-actuating member 44*. Communicationbetween the space 9i and the fluid inlet passage provides for the escapeinto such passage of fluid forced outwardly of the rotor past thepistons. The space 9| also permits equalization of the fluid levelwithin the inlet passage and the chamber portion of the casing enclosingthe bearing units I3 wherefore, when the pump is at rest, the lubricantfluid can supply a lubrication of these bearing units.

Upon an examination of Figs. 8 and 10, which are taken in differentdirections axially of the pump,'.it is ascertainable that, with therotor rotating in the direction indicated by the arrows in these twofigures, the pistons 42 will be moving radially outwardly while on thelower side of the pump casing, and will be moved inwardly whiletraversing the upper side of the pump caswherefore the fluid will beforced outwardly of the cylinder through said ports 46 and into theoutlet channel of the pump. The general operation is, therefore, thesame as that previously described with respect to the first embodiment.

The outer ends of thepis'tons 42 are curved similarly to the pistons 42of the first embodiment,

whereby the curved surfaces of these pistons are caused to rock upon theinner surface of the actuating member 64*, as well as slide thereon, andthis rocking motion of the pistons prevents the heat of friction beingapplied for any length of' time at a single line of contact between thepistons and actuating member. The actuating member 44 does not rotate sofreely upon the casing bearing 66 therefor as upon the ball bearing unit45 of the first embodiment, although there is a creeping movement of themember within the bearing 66, so that the entire inner surface of thismember 44 is ultimately subjected to the same character of pressure. andwear.

Attention is also called to the fact that the chamber 53 at the core ofthe rotor i5 has no communication with the high pressure outlet 'wardly,and, in this'manner, augment the centrifugal force upon the pistons forkeeping them constantly in contact with the actuating member 44 That theembodiment of the invention shown in Figs, 11 to 15 is identical to theembodiment in Figs. 7 to 10, except for certain differences, will beexpressly pointed out. Those parts in this embodiment which correspondto those in the first and third embodiments will be designated by thesame reference characters with the addition of the letter '0.

Small bolts 95 (not shown, but employed in the third embodiment) areemployed for attaching the wear plate 69 to the sealing member structure26. The inlet and outlet ports l8 and l9 in the casing end plate l6 areshaped somewhat diflerently from those in the third embodiment, and

this end plate l6 provides different accommodations for the headlessscrew 8 I for initially press- 7 ing the-sealing member structure 26against the 96 is placed about the stem of the sealing member structureand is slidable in the hole 66.

In this manner the pressure of fiuid in the outlet passage 15 is exertedthrough the sealing member onto the piston member 96 to cause thispassage of the pump, but this chamber 53 fills with fluid fromthecylinders 43 during operation of the pump because of the leakageinwardly past the tails 54 This leakage is augmented by an L-shapedchannel C in the tail of one of the pistons 42", this channel being ofsmall bore and shown in dotted outline in Fig. 8. The lateral leg CL ofthis channel C is disposed at such a distance from the inner end of thepiston as to be projected outwardly a very short distance from thebottom of the cylinder when the piston is at its outermost positionradially of the rotor, so that as the piston is subsequently forcedinward- 1y of the rotor, the high pressure communication between thecylinder and the chamber 53 through the channel C will be but for ashort time interval after which the lateral CL will be forced out ofcommunication with the cylinder Use of the channel C in. one or more ofthe piston tailscauses the chamber 53 to be filled quickly after thepump has been at rest and though the pump be initially driven at a slowspeed. A noncompressible fluid filling the chamber 53 will be operableto transmit pressure from the inwardly serve as pump plungers totransmit force throughthe body of the fluid" in the chamber 53 to thetails of those pistons which are to be moved Outpiston member to bearinwardly upon the enlarged part of the sealing member structure'26 forautomatically augmenting the force of the set-screw 8| for pressingtogether the slidable wear plates 69 and ll.

A further expedient shown in detail in Fig. 15 is used for pressing thesealing head structure 26 against the end of the rotor. A pair of bores91 are formed in the inner face of the holder 6l to reciprocally containplungers 98 for bearing against the outlet face of the enlarged portionof the sealing member 26. The inner ends of these bores 91 communicatewith the outlet passage through channels 99, wherefore the pressure offluidin the outlet passage is imposed upon the outer ends of theplungers 98 to cause them to bear inwardly against the sealing memberstructure and in this way increase the pressure which is applied theretofor urging it against the end of the rotor. and further to increase thearea over which the pressure is applied to the sealin "half of thatfigure. Under these circumstances the intake and discharge through thenormal ports and passages can be provided for by simply loosening thescrews 62 rotating the ring 63 and its appendages degrees, andretightening said screws. Index arrows A and B, Fig. 11, spaced 180degrees about the holder 6| are respectively alinable with the arrow Con the casing in the two adjustments for opposite direction drive of.

11' to expedite this description, those parts identical with orcorresponding to parts in the first embodiment are designated by thesame respective reference numerals with the letter (1 added.

In this final embodiment, the rotor I includes a thick end plate IIIhaving a conical end face 28 The ports 46 leading from the cylinders 43communicate through said end plate II I to the conical surface 28 Theend plate is connected to the main body of the rotor I5 by machine boltsH2. The sealing member 2I5 has a conical sealing face 2'l formed insliding sealing relation with the conical face 28 and this sealingmember is secured in a recess I I3 of the pump casing by means of bolts(not shown), so that this sealing member will be held against rotationwith the rotor. An inlet port IIl in the pump casing communicatesthrough a channel 49 with an inlet port 41 in the conical sealingmember, whereas an outlet port I9 in the casing communicates through achannel 5| with an outlet port 48 in said sealing member. In Fig. 17,the inlet and outlet ports 41 and 48 are shown in a manner displayingtheir geometric arrangement upon the sealing member and their respectivecircumferential extent thereabout.

The outlet port 48 in the sealing member is intersected by a channel H4formed coaxially with the sealing member and coaxially with a channel 55in the rotor This latter channel and the channel H4 have enlargedadjacent end sections which fit in close sliding relation with a tubeH5, so that said channels and the tube H5 provide communication betweenthe high pressure outlet port 48 and the center chamber 53 in the rotor.Fluid under pressure is thereby maintained upon the inner ends of thepiston tails 54 to supplement centrifugal force in holding the pistonsoutwardly in sliding relation with their bearing surface upon theeccentrically mounted pistonactuating member M during rotationof thepump rotor and of said piston-actuating member. Any leakage occurringbetween the tube H5 and the side walls of the channels 55 and H4 into aspace H6 between the end of the sealing member and the left end of themain body of the rotor I5 is conducted back to the inlet port 41 througha small channel III. Any leakage occurring between the conical sealingsurfaces 2'! and 28 in an axial forward direction into the space H6 issimilarly conducted into the inlet port 41 and leakage axiallyrearwardly between the surfaces 21 and 28' will pass through a space I I8 between the left end of the casing and the left end of the rotor endplate III into the casing. Fluid thus accumulating in the casing,andfluid accumulating in the casing because of leakage radiallyoutwardly between the pistons 42 and their cylinders 43 when attaining asufficient amount, is drained into the inlet channel '49 through a shortpassage I IS.

A further distinction between this last embodiment of the invention andthe first embodiment is in the increased length of the reentrant casingportion I2 for supporting a pair of axially spaced ball bearing units 45and 45 for the rotative support of the piston-actuating member 44. Theconical surface 2I provides a bearing support for the rotor and thuscooperates with the ball bearing unit I2I for rotatably supporting therotor I5 and the drive shaft W A hole I34 through the casing reentrantportion I2 is slightly oversize with respect to the shaft M so that itwill not complicate proper alining of the shaft and rotor upon theirhearing supports.

12 The desired pressure between the sealing surfaces 21 and 28 ismaintained by an adjustable thrust-exerting means comprising a ballbearing unit I2I, having its inner race mounted upon the drive shaft Magainst a shoulder I22 thereof. The outer race of this ball bearing unitis mounted within a ring I23 having a cylindrical portion I 24 slidablewithin a recess I25 in the right end wall of the casing and a threadedsection I26 tumable into a threaded sect-ion I21 at the outer end of therecess. The desired adjustment for the sealing surfaces 21 and 28 isaccomplished by first loosening a set-screw I28, and thus loosening abrass friction member I29 from the cylindrical surface I24 of the ringI23. Thereafter, the ring I23 may be rotated by the use of a spannerwrench engageable with end recesses I3I in said ring, providing a gearI32 is not then assembled with the drive shaft I4. Should this gear I32be assembled on the shaft M when the adjustment is made, holes I33 inthis gear, which are axially alinable respectively with the recesses I3|, are capable of coreceiving therewith short rods or the like to causethe ring I23 to be rotatively adjusted by simply rotating the gear.After the adjustment is made these rods will be withdrawn and theset-screw I28 'retightened.

The operation of this pump is identical to that of the first embodiment.It is, therefore, not repeated at this point.

While I have herein shown and described preferred embodiments with theview of illustrating the invention, it should be understood that theinvention extends to other forms, arrangements, structures and detailsfalling withinthe scope and spirit thereof and not sacrificing all ofits material advantages.

What is claimed is:

1. In a pump, a rotor having radially directed cylinders opening intoits outer periphery, ports communicating with such cylinders, a closedfluid-containing chamber centrally of the cylinders, and borescommunicating between the cylinders and said chamber; pistonsreciprocable in said cylinders with an in and out motion radially of therotor and comprising auxiliary portions disposed reciprocably in saidbores to communicatively isolate their cylinders from said chamber andin pressure imposing relation with the fluid in said chamber; a memberhaving a circular force-reaction surface circumscribing the rotor ineccentric relation with the rotor axis to restrain outward axialmovement of the pistons by the action of centrifugal force thereonduring rotation of th rotor and to complement such centrifugal force incausing in and .out pumping action of the pistons and their auxiliaryportions respectively in said cylinders and said bores; and the chamberbeing operable through the medium of said fluid therein to transmitforce from each auxiliary piston portion, as it is moved inwardly,outwardly upon the other piston portions for supplementing thecentrifugal force in constantly maintaining the pistons in outward forceexerting relation with the ring-like member.

2. In a pump, a rotor having radially directed cylinders opening intoits outer periphery, ports communicating with such cylinders, a closedfluid-containing chamber centrally of the cylinders, and bores of lessdiameter than said cylinders projecting axially therefrom inwardly intocommunication with said chamber; pistons re- -13 motion radially of therotor and comprising tail portions on their inner ends projecting intosaid bores for like motion and for communicatively isolating thecylinders from said chamber, a

member having a circular force reaction surface circumscribing the rotorin eccentric relation with the rotor axis to restrain outward axialmovement of the. pistons by the action of centrifugal force thereonduring rotation of the rotor and to complement such centrifugal force incausing in'and out pumping action of the pistons and their tail portionsrespectively in said cylinders and said bors; and the chamber beingoperable through the medium of said fluid therein to transmit force fromeach piston tail portion, as it is moved inwardly, outwardly upon theother tail portions for supplementing the centrifugal force inconstantly maintaining the pistons in outward force exerting relationwith the ring-like member.

3. In a rotary pump of the piston type, a rotor having radial cylindersand counter-bores in the radially inner ends of said cylinders, pistonsin said cylinders to cooperate therewith in forming pumping chambers andreciprocable in their respective cylinders to cause expansion andcontraction of said chambers, there being ports respectivelycommunicating with said chambers for accommodating ingress and egress offluid to and from said chamberspursuant to such reciprocation of thepistons, tail portions on said-pistons projecting into saidcounter-bores, and a piston actuating member having a surfaceeccentrically oircums'cribing the rotor to restrain outward movement ofthe pistons in a variable amount and to thus complement the centrifugalforce on the pistons to cause in and out pumping motion of the pistonsduring rotation of the rotor.

' 4. In a rotary pump of the piston type having an inlet duct and adischarge duct through which fluid is discharged from the pump underpressure, a rotor having radial cylinders and counter-bores in thebottoms of said cylinders, pistons reciprocable in said cylinders topump fluid into the discharge duct,'tail portions on said pistons andprojecting into said counter-bores for reciprocation therein pursuant tosaid reciprocation of the pistons a piston actua ing member having asurface eccentrically circumscribing th rotor to restrain outwardmovement of the pistons in a variable amount and to thus complement thecentrifugal force on the pistons to cause reciprocation of the pistonsand tails during rotation of the rotor, means providing communicationbetween the cylinders and the inlet duct during outward movement of thepistons and communication between the cylinders and the discharge ductduring inward movement of the pis ons. and channel means communicativebetween said discharge duct and the counter-bores to impose fluid underpressure against the ends of the piston tails and thus augment thecentrifugal force in urging the pistons radia ly outwardly,

5. In a rotary pump of the piston type having an inlet duct and adischarge duct through whichfluid is discharged from the pump underpressure, a rotor having radial cylinders and counterbores in thebottoms of said cylinders. pistons reoiprocable in said cylinders tocause'withdrawal of fluid from the inlet duct and delivery thereof intothe discharge duct, tail portions on said pistons and nroiecting intosaid counter lcores for reciprocation therein pursuant to saidreciprocation of the pistons, a piston actuating member having a surfaceeccentrically circumscribing the rotor to restrain outward movement ofthe pis- 14 tons in a variable amount and to with the centrifugal forceon the'pistons to cause reciprocation of the pistons and tails duringrotation of therotor, means providing communi- "cation between thecylinders and the inlet duct during outward movement of thefpistons andcommunication between the cylindrsand the discharge duct during inwardmovement of the pistons, said rotor having a cavity with which saidcounter-bores communicate, and channel means communicative between, thepump discharge duct and the counter-bores through said cavity to imposefluid under pressure against the ends of the piston tails and thus'augment the centrifugal force in urging the pistons radially voutwardly.

6; In a pump, a rotor cylinders opening into its outer periphery, an endface, ports communicating between bottom portions of the cylinders andpositions on said end face spaced radially and circumferentially fromthe rotor axis, a closed chamber centrally of the cylinders, and borescommunicating between the cylinders and said chamber; pistons re-'ciprocable in the cylinders with an in and out motion radially of therotor and comprising auxiliary portions projecting into. said bores forlike in and out motion and for communicativelyjisolating the cylindersfrom saidchamber; a, member having a circular force reaction surfacecircumscribing the rotor in eccentric relation with the rotor axis torestrain outward axial movement of the pistons by the action ofcentrifugal force thereon during rotation of its-rotor and to coact withsaid centrifugal force in causing outward movement of the pistons whilethey and their cylinder ports traverse an intake portion or their pathof revolution about the rotor axis and in causing inward movement whilethey and their cylinder ports traverse a discharge portion of said path;a fluid discharge line including an apertured sealing member; meansmaintaining said sealing member in sliding. sealing relation I with therotor and face while maintaining the aperture in registry with thecylinder ports while they traverse the discharge portion of said path;inlet duct means communicating with said ports only while they traversethe intake portion of said path; and duct means communicating betweenthe rotor chamber and said discharge line to conduct fluid underpressure into said chamber for pressing outwardly upon the pistonauxiliary portions.

'T. In combination, a pump casing, a. rotary pumping unit in said casingand having a ported end face for the inlet and discharge ofa'lubrieating fiuid, bearing means for said unit and disposed in thecasing for lubrication bysuch fluid in' the casing, and said casingincluding a wall having a portion in sliding sealing relation with thepumping unit end face, said wall providing discharge passage meansdisposed for successive communicative registration by the ports of saidend face during a cyclical phase in the rotation of the unit, said wallalso providing inlet passage means communicative with the interior ofthe casing to provide for delivery of the lubricating fluid thereintoand also disposed for suc- .cessive communicative registration with saidthereof and having a ported end face for the inlet thus cooperate havingradially directed.

l and discharge of fluid to and from said cylinders, pistonsreciprocable in the cylinders to draw fluid thereinto through theirrespective ports in the end face during outward movement and todischarge the fluid from the cylinders through said ports during inwardmovement, part of the fluid leaking past the pistons and through thecylinder end openings into the casing during such discharge, means forreciprocating the pistons to cause their outward movement during thetraversal of an inlet portion of a circular path followed by said portsduring rotation of the rotor and to cause inward movement during thetraversal of an outlet portion of such path, and said casing including awall having a portion in sliding sealing relation with the rotor endface, said wall providing discharge passage means disposed forcommunicative registration with said ports during their traversal of theoutlet path portion, said wall also providing inlet passage meanscommunicative with the interior of the casing to drain said leakagefluid therefrom and also disposed for communicative registration withthe rotor ports during their traversal of the inlet path portion.

9. In a rotary pump of the piston type, a pump casing comprising opposedwalls, a rotor bearing in one of said walls, a rotor shaft rotativelycarried on said bearing, a rotor in said casing constrained for rotationwith said shaft and spaced axially from the one wall to provide alubricant conducting passage for conducting lubricant from the casingonto said bearing, said rotor having radial cylinders opening outwardlyin the periphery thereof and having a ported end face for the inlet anddischarge of a lubricating liquid into and from said cylinders, therebeing clearance between said periphery of the rotor and the easing sothat liquid can flow therein exteriorly of a the rotor from either endof the rotor to the other, pistons reciprocable in the cylinders to drawsuch liquid thereinto through their respective ports in said end faceduring outward movement and to discharge the liquid from the cylindersthrough said ports during inward movement, part of the liquid leakingpast the pistons and outwardly through the cylinders into the casing,means for reciprocating the pistons to cause their outward movementduring the traversal of an inlet portion of a circular path followed bysaid ports during rotation of the rotor and to cause inward movementduring the traversal of an outlet portion of such path, and the otherwall of saizl casing including a portion in sliding sealing relationwith the rotor end face, said wall providing discharge passage meansdisposed for communicative registration with said ports during theirtraversal of the outlet path portion, said wall also providing inletpassage means communicative with the interior of the casing to supplysuch liquid thereto exteriorly 0f the rotor and to drain any excesstherefrom caused by said leakage past the pistons, and said inletpassage means also being disposed for communicative registration withthe rotor ports during their traversal of the inlet path portion. v

10. In a rotary pump of the piston type, a pump casing comprisingopposed walls, a rotor bearing in one of said walls, a rotor shaftrotatively carried on said bearing,a rotor in said casing constrainedfor rotation with said shaft and spaced axially from the one walltoprovide a lubricant conducting passage for conducting lubricant fromthe casing onto said bearing, said rotor having radia1 cylinders-openingoutwardly in the periphery thereof and having a ported end a face forthe inlet and discharge of a lubricating liquid into and from saidcylinders, pistons reciprocable in the cylinders to draw such liquid 5thereinto through their respective ports in said end face during outwardmovement and to discharge the liquid from the cylinders through saidports during inward movement, part of the liquid leaking past thepistons and outwardly through the cylinders into the casing, an annularpiston actuating member journaled in the casing eccentrically of therotor and having an annular surface circumscribing said rotary peripheryto bear against said pistons and thus complement centrifugal forceacting thereon to cause said inward and outward motion thereof duringrotation of the rotor, there being a clearance space between saidperiphery of the rotor and the piston actuating member and through whichthe 20 end thereof to the other, the other casing wall including aportion in sliding sealing relation with the rotor end face, said otherwall providing discharge passage means disposed forcommunicativeregistry with the rotor ports during inward movement of their associatedpistons, said other wall also providing inlet passage meanscommunicative with the interior of the casing to supply such liquidthereto exteriorly of the rotor and to drain any excess therefrom causedby leakage past the pistons, and said inlet passage means also beingdisposed for communicative registration with the rotor ports duringtheir traversal of the inlet path portion.

11. In a pump, a casing having a threaded section with threads directedcircumferentially of the casing, a pumping unit in said casing andhaving a fluid discharge station oriented circumferentially of thecasing, a ported discharge mem- 40 ber for disposition at such stationfor conducting the discharged fluid therefrom, and means for disposingthe ported member at said station, comprising an orientation memberhaving a section with threads meshable with and rotatable in the casingthreaded section, a holder for the ported member attachable to theorientation member and orientated pursuant to said rotation to disposethe ported member at the discharge station, tension exerting meansconnected between said orientation member and said holder member fordrawing the latter toward the former, and means reactable through thecasing to limit the approach of said members and being thus cooperablewith the tension exerting means to create an axial stress upon'themeshed threads.

12. In a pump, a casing, a pumping unit in said casing and having afluid discharge station oriented circumferentially of the casing, aported discharge member for disposition at such station for conductingdischarged fluid therefrom, and an assemblyfor disposing the portedmemher at said station, comprising an orientation member rotatablecircumferentially of the casing, a holder for the ported memberattachable to the orientation member and orientated pursuant to saidrotation to dispose the ported member at the discharge station, tensionexerting means connected between the orientation member and said holdermember for drawing the latter toward the former, and means comprisingmeshable counterparts respectively upon one of the two last-namedmembers and the casing cooperable with said tension exerting means toprevent rotation of the said members relatively to the casing when saidholder member and said liquid can flow exteriorly of the rotor fromeither 17 orientation member are drawn toward one another as aforesaid.

13. In a pump, a casing,.a pumping unit in said casing and having afluid discharge station oriented circumferentially of the casing, aported discharge member for disposition at suchstation for conductingdischarged fluidtherefrom, and an assembly for disposing the portedmember at said station, comprising an orientation member rotatablecircumferentially of the casing, a holder for the ported memberattachable to the orientation member and orientated pursuant to saidrotation to dispose the ported member at the dis charge station, meanspreventing simple displacement of the orientation member axially of thecasing, and tension exerting means connected between the orientationmember and the holder member to draw the latter toward said orientationmember and into force imposing relation.

with the casing to tighten said assembly.

14. In a pump, a casing having an index means thereon, a pumping unithaving a fluid discharge station occupying respectively differentpositions circumferentially of the casing when driven in oppositedirections, a ported discharge member for disposition at either of saidstations for conducting discharged fluid therefrom, and an assembly forselectively disposing the ported member at said stations, comprising anorientation member rotatable circumferentially of the casing, a holderfor the ported member attachable to the orientation member and rotatablethere-' with to dispose the ported member at either of said stations,index means rotatable with said holder member for complementaldisposition with respect to the casing index means to indicate thestation at which the discharge member is disposed, tension exertingmeans connected between the orientation member and said holder memberfor drawing the latter toward the former, andmeans comprising meshablecounterparts respectively upon one of the two last-named members and thecasing cooperable with said tension exerting means to prevent rotationof the said members relatively to'the casing when said holder member andsaid orientation member are drawn toward one another as aforesaid.

15. In a pump, a casing having a reentrant end wall portion containingan opening directed axially of the casing and an exterior bearinggenerated about an axis parallel to that of the opening but eccentricwith respect thereto, a pumprotor shaft extending through said opening,a pump rotor in the casing and constrained for rotation with the shaft,said rotor containing radial cylinders opening outwardly of itsperiphery and an end face disposed oppositely to the shaft andcontaining ports leading respectively from bottom portions of thecylinders, pistons in said cylinders, said pistons having outer endsprojecting outwardly beyond the rotor periphery, a piston actuatingmember rotatively supported on the exterior bearing of said reentrantcasing portion and having an internal surface embracing the rotorperiphery for rotation eccentrically thereof and concentrically of saidexterior bearing tolimit outward movement of the pistons while they andtheir ports traverse an inlet portion of their path of revolution and toforce said pistons in wardly while they traverse an outlet portion ofsaid path during rotation of the rotor, and ported means having inletand outlet ports disposed for communication with the rotor portsrespectively while they traverse their inlet and outlet path portions.

16. In a pump, a casing having a reentrant end wall portion containingan opening directed axially of the casing and an exterior surfacegene1-,

ated about an axis parallel to that of the opening but eccentric withrespect thereto, a pump-rotor shaft extending through said opening, apump rotor in the casing and constrained for rotation with the shaft,said rotor containing radial cylinders opening outwardly of itsperiphery and an end face disposed oppositely to the shaft andcontaining ports leading respectively from bottom portions of thecylinders, pistons insaid cylinders, said pistons having outer endsprojecting outwardly beyond the rotor periphery. axially spaced bearingunits mounted on the exterior surface of said reentrant casing portion,a piston actuating member supported on said bearing units for rotationabout said eccentric axis, said actu ating member having an internalsurface embracing the rotor periphery to limit outward movement of thepistons .while they and their ports traverse an inlet portion in theirpath of revolution and to force said pistons inwardly while theytraverse an outlet portion of said path during rotation of the rotor,ported sealing means against which the rotor end face is axiallypressable and providing inlet and outlet ports disposed forcommunication with the rotor ports respectively while they traversetheir inlet and outlet path portions, and means on said casing at theouter end of said reentrant portion for adjusting the rotor shaftaxially to determine the pressure between the rotor end face and thesealing member.

1'7. In a pump, a rotor having radial cylinders opening radiallyoutwardly thereof, radial bores in the bottoms of the cylinders, portsleading from bottom portions of the cylinders into an end face of suchrotor, and channel means communicating with said bores and leadinginwardly from said end face coaxially with said rotor, pistons in saidcylinders, tails on said pistons projecting into said bores, a pistonactuator having a surface eccentrically embracing the rotor to limitoutward movement of the pistons during their traversal of an inletportion of them and their ports in their path of revolution duringrotation of the rotor and to force said pistons inwardly during theirtraversal of an outlet portion in said path of revolution, means havinginlet and outlet ducts disposed for communication with the rotor portsrespectively while they traverse said inlet path portion and said outletpath portion and having a lateral communicating with the outlet duct andarranged in opposed coaxial relation with the rotor channel means, and atube disposed in said lateral and said channel to complete communicationbetween the outlet duct and the rotor bores to provide fluid thereinunder pressure for urging the pistons against the surface of saidactuating. member.

18. In a pump, a casing having a bearing in a wall thereof, a driveshaft extending into said casing and rotatably supported upon saidbearing, a pumping unit constrained for rotation with said shaft andhaving a conical end face disposed oppositely from said bearing andcontaining circumferentially spaced ports in said face through whichfluid is received into the unit during their traversal of an inletportion of a path of revolution about the axis of said unit duringrotation thereof and through which ports the received fluid isdischarged from the unit during their traversal of an outlet portion ofsuch path of revolution, a sealing member supported on said cas- 19 ingcoaxially with the rotor and having a conical bearing and sealingsurface disposed within the conical end face of the rotor forcooperating with said bearing in the support of the rotor, said conicalmember containing circumferentiallyspaced inlet and outlet ports in theconical surface thereof, said inlet port being disposed for registrationwith the ports of the unit during their traversal of said inlet pathportion and said outlet port being disposed for registration with theports of the unit during their traversal of said discharge path portion,and adjustable means for retaining said pumping unit and said sealingmember axially together with said end face and the conical surface ofsaid sealing member in sliding sealing journaled relation.

19. In a rotary pump of the piston type, a'rotor having radial cylindersand intercommunicative counter-bores at the bottoms of said cylinders,pistons reciprocable in said cylinders, tail portions on said pistonsprojecting into said counterbores, a piston-actuating member having asurface eccentrically circumscribing the rotor to restrain outwardmovement of the pistons in a variable amount during rotation of therotor and. being thus cooperable with the centrifugal force on thepistons to cause in and out pumping motion thereof, and at least one ofsaid tail portions containing a channel communicative between saidcounter-bores and a side wall portion of such tail portion thatcommunicates with the associated cylinder when the associated piston isin a position radially outwardly of the rotor.

20. In a rotary pump of the piston type, a rotor having radial cylindersopening into its outer periphery, ports communicating with inner endportions of the cylinders, a chamber, and bores communicating betweenthe inner ends of the cylinders and said chamber, said ports having apath of revolution about the rotational axis of the rotor; pistonsreciprocable in said cylinders and comprising auxiliary portionsdisposed reciprocably in said bores to at least throttle communicatlonbetween their respective associated cylinders and said chamber, meansfor reciprocating the pistons relatively to the cylinders, coordinatelywith rotor rotation, to cause movement of the pistons outwardly of theircylinders to an outer limit and consequent ingress of fluid through theports while they traverse an inlet zone in their path of revolution andto cause inward movement of the pistons from such limit and consequentcompression of the fluid in the.

cylinders and egress through their ports while they traverse an outletzone in their path of revolution, and channel means communicativebetween said chamber and at least one of said cylinders during thecompression of fluid therein to insure provision of a. sufficientquantity of fluid in said chamber for transmitting force from inwardlymoving cylinder auxiliary portions to the outwardly moving of suchportions to urge the same outwardly.

' CARL W. MOTT.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 297,329 Wiegand Apr. 22, 18841,087,181 Pitman Feb. 17, 1914 1,325,434 Carey et a1 Dec. 16, 19191,515,529 Well Nov. 11, 1924 1,635,006 Oliver July 5, 1927 1,778,238Wilsey Oct. 14, 1930 1,817,063 Carrie et al Aug. 4, 1931 2,103,314Benedek Dec. 28, 1937 2,273,468 Ferris Feb. 17, 1942 2,245,570Centervall June 17, 1942 FOREIGN PATENTS Number Country Date 124,069Great Britain Mar. 20, 1919 406,106 Great Britain Feb.22, 1934

